ES2216245T3 - FRIDGE APPARATUS - Google Patents

Abstract

A COOLING DEVICE (81-91) THAT MAKES USE OF A NON-AZEOTROPIC REFRIGERANT AND INCLUDES A VARIABLE CAPACITY COMPRESSOR (1), A HEAT CHANGER OF A HEAT SOURCE (5), A REGULATING DEVICE (4), A CHANGER HEAT ON THE USER'S SIDE (13), A DETECTION DEVICE FOR A REFRIGERANT CYCLING COMPOSITION (15). THE CYCLE COMPOSITION DETECTED IS USED TO DETERMINE THE CONDITION OF THE INTERIOR OF THE REFRIGERATION DEVICE; IN ADDITION, TO PREVENT THAT THE APPLIANCE WORKS BAD, THE REFRIGERATION APPLIANCE (81-91) INCLUDES DETECTORS (24,28,35,36,37) TO DIRECTLY DETECT PARAMETERS THAT CANNOT BE DETERMINED WITH ACCURACY DUE TO AN ERROR OR SIMILAR IN THE DETECTION OF THE REFRIGERANT CYCLING COMPOSITION.

Description

Refrigerator

The present invention relates to an apparatus of refrigeration using a non-azeotropic refrigerant, according to the preamble of claim 1. Such apparatus is known, by example, by EPA-0 586 193.

Figure 15 is a refrigeration apparatus conventional in which a non-azeotropic refrigerant is used and which is described, for example, in the Japanese Patent Application published number 75280/1996. This refrigeration appliance is provided with a refrigerant circuit in which a compressor 1, a condenser 3, a first capillary tube 4, an evaporator 5, and a accumulator 6 are sequentially connected in loop form by the tube and in which a non-azeotropic refrigerant circulates; a tube bypass 8 bypass the refrigerant circuit from the tube between the compressor 1 and the condenser 3 to the tube between the compressor and evaporator and in which means are connected cooling 9 and a second capillary tube 10; a detector of temperature 12 and a pressure detector 13 to detect the temperature and pressure of an outlet portion of the second tube capillary; and a composition calculator 14 to calculate the composition of the refrigerant circulating in the circuit refrigerant. The composition of the refrigerant circulating in the refrigerant circuit can be calculated in this device cooling, and the operation of the refrigeration apparatus is controls based on this refrigerant composition.

However, with conventional technology, no there has been no method to maintain the condensation temperature and evaporation temperature at fixed levels as a means to properly control the operation of the refrigeration apparatus using a non-azeotropic refrigerant. Namely, since the condensing temperature and evaporation temperature have determined with the fixed cyclic composition or with the cyclic composition set for each operating condition, has been impossible to follow, or follow sufficiently, the changes of the condensing temperature and evaporation temperature with regarding changes in the cyclic composition. In addition, it has been impossible to demonstrate a predetermined capacity at escape time gas or wrong refrigerant charge.

In addition, with the cooling device that use a non-azeotropic refrigerant, if the composition changes Cyclic refrigerant, condensing pressure and pressure evaporation changes in a case where the temperature changes of condensation and evaporation temperature. For this reason, the coolant circuit flow rate changes, so that it is impossible to guarantee a stable capacity, and it is difficult to guarantee subcooling on the input side of a device constriction. Namely, there has been a compatibility issue by guaranteeing subcooling and guaranteeing the flow refrigerant.

In addition, with the cooling device that also uses a non-azeotropic refrigerant, in the operation to low outside air temperature, since the refrigerant that left the compressor condenses on the refrigerant tube where it coolant cools, the amount of coolant supplied to the compressor is temporarily smaller than the amount of refrigerant leaving the compressor, with the result that the pressure inside the suction portion of the compressor, which results in the malfunction of the compressor.

In addition, since the pressure is higher for R.407C that R.22 at the same temperature, the malfunction of the refrigeration apparatus due to excessive pressure rise in the discharge portion of the compressor is more prone than produce in the case of the refrigeration device using R.407C that in the case of the refrigeration apparatus that uses R.22.

Also, with R.407C refrigerant, the bad compressor operation due to corona discharge under vacuum it tends to occur more than with R.22 refrigerant.

In addition, with the cooling device that uses R.407C refrigerant and ester oil and ether oil which are Used refrigerant machine oils for R.407, is more prone that occur in large quantities sludge that affect adversely to the refrigeration apparatus.

In addition, with the non-azeotropic refrigerant, it has it was impossible to accurately detect the compression of the refrigerant in the compressor, with the result that it is prone that a malfunction occurs in the compressor.

In addition, with the non-azeotropic refrigerant, it has it was impossible to detect superheat exactly Excessive compressor on the discharge side of the compressor.

In addition, with the non-azeotropic refrigerant, it has it was impossible to accurately detect a decrease in concentration of the lubricating oil in the compressor due to excessive supply of coolant.

In addition, with the non-azeotropic refrigerant, it has it was difficult to get subcooling at the exit of condenser.

The present invention has the purpose of overcome the problems described above, and its purpose is to make possible use a non-azeotropic refrigerant without problem (including a pseudo-azeotropic refrigerant) in a device refrigeration.

According to the present invention, a refrigeration apparatus as set forth in claim 1.

Preferred and optional features are set forth in the dependent claims.

In the attached drawings:

Figure 1 is a diagram of a circuit of refrigerant according to a first embodiment of the present invention.

Figure 2 is a Mollier diagram illustrating changes of a refrigerant in a detector device cyclic composition according to the first embodiment of the present invention.

Figure 3 is a diagram of a circuit of refrigerant according to a second embodiment of the present invention.

Figure 4 is a diagram of a circuit of refrigerant according to a third embodiment of the present invention.

Figure 5 is a diagram of a portion of connection between an accumulator and a bypass pipe for a gas high temperature refrigerant.

Figure 6 is a diagram of a circuit of refrigerant according to a fourth embodiment of the present invention.

Figure 7 is a diagram of a circuit of refrigerant according to a fifth embodiment of the present invention.

Figure 8 is a diagram of a circuit of refrigerant according to a sixth embodiment of the present invention.

Figure 9 is a diagram of a circuit of refrigerant according to a seventh embodiment of the present invention.

Figure 10 is a diagram of a circuit of refrigerant according to a modification of the seventh embodiment of the present invention

Figure 11 is a control flow diagram according to the modification of the seventh embodiment of the present invention.

Figure 12 is a diagram of a circuit of refrigerant according to an eighth embodiment of the present invention.

Figure 13 is a diagram of a circuit of refrigerant according to a ninth embodiment of the present invention.

Figure 14 is a diagram of a circuit of refrigerant according to a tenth embodiment of the present invention.

And Figure 15 is a diagram of a circuit of refrigerant according to conventional technique.

Detailed description of the preferred embodiments

First realization

Figure 1 illustrates a refrigeration apparatus 81 which is an example of the refrigeration apparatus and of air conditioning using a non-refrigerant azeotropic according to the present invention. In this device of cooling 81, a compressor of variable capacity 1, a valve four-way 2, an indoor unit heat exchanger 3 that It is a use side heat exchanger, a first device choke 4, an outdoor unit heat exchanger 5 that It is a heat exchanger unit side heat exchanger, a accumulator 6, and compressor 1 are connected in series in this order through the tubes, thus forming a refrigerant circuit. At the same time, through a change made by the valve four-way, compressor 1, four-way valve 2, the outdoor unit heat exchanger 5, the first device throttling 4, the indoor unit heat exchanger 3, the accumulator 6, and compressor 1 are connected in series in this order by the tubes, thus forming another circuit of refrigerant. In addition, the refrigeration apparatus 81 is provided of a detector device of cyclic composition 15, a first pressure detector 16 disposed in a discharge tube of the compressor 1, and a second pressure detector 13 arranged in a compressor suction tube 1. In addition, the heat exchanger outdoor unit is equipped with a capacity fan variable 7, and a speed output device is provided Rotary fan / compressor frequency 17, which are about variable capacity fan / compressor means to send the rotational speed of fan 7 and compressor frequency 1. Variable capacity media can be formed separately as the means of varying capacity of the fan and the means of variable compressor capacity.

In addition, R.407C, which is a non-refrigerant azeotropic in which R.32, R.125, and R.134a are mixed at a ratio of 23% by weight, 25% by weight, and 52% by weight, is loaded into the cooling apparatus 81 represented in figure 1.

In the drawing, the dotted lines show that control values are sent in the directions of the arrows.

Next, the operation of the cooling device 81. During heating, the high pressure and high temperature gas refrigerant which is Discharged from compressor 1 flows to the unit heat exchanger inside 3 via the four-way valve 2, and condenses and liquefied when cooled by air at ordinary temperature and analogues The refrigerant leaving the unit heat exchanger interior 3 experiences pressure reduction for the first throttle device 4, and flows to the heat exchanger outdoor unit 5. In the outdoor unit heat exchanger 5, low temperature is produced, the refrigerant evaporates, gasifies, and leaves, and the refrigerant gas flows to the accumulator 6 using the four-way valve 2, and is sucked into the compressor 1 after passing through the accumulator 6. The excess refrigerant in cooling device 81 is present inside the accumulator 6 in the form of liquid refrigerant. So, the temperature of condensation of the indoor unit heat exchanger and the evaporation temperature of the unit heat exchanger outside can be changed by changing the rotational speed of the fan 7 and changing the rotational speed by changing the compressor frequency 1.

During cooling, the refrigerant gas to high pressure and high temperature that is discharged from the compressor 1 flows to the outdoor unit heat exchanger 5 through the four-way valve 2, and condenses and liquefies when cooled by the air at ordinary temperature and the like. The refrigerant that came out of the outdoor unit heat exchanger 5 experiences reduction of the pressure through the throttle device 4, and flows to the indoor unit heat exchanger 3. In the heat exchanger of indoor unit 3, low temperature is produced, the refrigerant evaporates, gasifies, and leaves, and the refrigerant gas flows to the accumulator 6 via the four-way valve 2, and is sucked into the compressor 1 after going through accumulator 6. Then, the condensing temperature of the unit heat exchanger outside and evaporation temperature of the heat exchanger indoor unit can be changed by changing the rotational speed of fan 7 and changing the rotational speed by changing the compressor frequency 1.

Next, the operation of the detector device of cyclic composition 15. In Figure 1, the reference number 8 denotes a bypass tube that puts in bypass the discharge tube of the compressor 1 and the tube of compressor suction; 9, a first tube heat exchanger double; 10, a first pressure reducing device; 11, a first temperature sensing device; 12, a second detector of temperature; 13, a second pressure detector; 14, a device of composition calculation. Said component parts, that is, the bypass tube 8, the first double tube heat exchanger 9; the first pressure reducing device 10, the first detector of temperature 11, the second temperature detector 12, the second pressure detector 13, and the calculation device of composition 14, constitute the composition detecting device cyclic 15.

Part of the high pressure gas refrigerant that out of the compressor 1 goes through the bypass tube 8, experience thermal exchange with the low pressure refrigerant in the first double tube heat exchanger 9 where it is liquefied. After the coolant is subjected to pressure reduction in the first pressure reducing device 10, and a Biphasic refrigerant at low pressure. Then the refrigerant Biphasic experiences thermal exchange with the refrigerant at high pressure in the first double tube heat exchanger 9, evaporates, and gasify before returning to the suction side of compressor 1. In this device, the temperature of the coolant in the first temperature detector 11 and the temperature and pressure of the two-phase refrigerant in the second temperature detector 12 and the second pressure detector 13 are detected (since the value of the second pressure detector 13 and the outlet pressure in the first pressure reducing device 10 are substantially equal, the outlet pressure of the first reducing device of pressure 10 is set as the value of the second pressure detector 13). Based on the temperature and pressure, the cyclic composition of the non-azeotropic refrigerant in refrigeration apparatus 81 is calculated and detected by the composition calculation device 14. The detection of this cyclic composition is carried out constantly while the refrigeration apparatus and of air conditioning receives power.

Here, the method of calculating the cyclic composition of the refrigerant. Since R.407C is a mixed non-azeotropic refrigerant of three types, and all three Types of components of the cyclic refrigerant composition are unknown, if three equations are formulated, and if they are solved, the unknown components of the cyclic composition may be known. However, if all three types of components are joined  cyclic, the result is 1. Therefore, if R.32 is expressed as a32, R.125 as a125, and R.134a as a134a, the following formula:

(1) a32 + a125 + a134a = one

Therefore, if two equations are formulated (excluding the above formula a32 + a125 + a134a = 1) with respect to two unknown types of cyclic components, and if solve, cyclic components may be known. By example, if you can formulate two equations in which a32 and a125 are not known, cyclic components can be known.

Next, the method of formulating the equations in which a32 and a125 are unknown.

First, the first equation can be formulate from the cyclic composition detector device 15 represented in figure 1. Figure 2 is a Mollier diagram which illustrates changes in refrigerant status in the device cyclic composition detector 15. In the drawing, 1) shows the state of the high pressure gas refrigerant that left the compressor one; 2) shows the state in which the gas refrigerant has Experienced heat exchange with low pressure refrigerant in the double tube heat exchanger 9 and it has been liquefied; 3) shows the state in which the coolant has been subjected to reducing the pressure in the first reducing device of pressure 10, and has become a two-phase refrigerant under pressure  low; and 4) shows the state in which the biphasic refrigerant has Experienced heat exchange with refrigerant at high pressure in the double tube heat exchanger 9, and it has evaporated and gasified. Since the enthalpies in 2) and 3) in the Figure 2 are the same, it is possible to formulate an equation in which a32 and a125 are not known and the enthalpies in 2) and 3) are the same. TO know, if the enthalpy in 2) is supposed to be h1, the enthalpy in 3) is ht, the temperature detected by the first detector of temperature 11 is T11, the temperature detected by the second temperature detector 12 is T12, and the pressure detected by the pressure detector 13 is P13, it is possible to derive the equation next:

(2) h1 (a32, a125, T11) = ht (a32, a125, T12, P13)

In the second equation, to the extent that the refrigerant initially charged in the refrigeration apparatus is R.407C, a gas-liquid balance is valid, and there are fixed relationships between the components of the composition cyclic even when the liquid accumulates in the accumulator and after the refrigerant leak has occurred. Namely, if A and B are assumed to be constant, it is possible to formulate the following experimental formula on equilibrium composition gas-liquid:

(3) a32 = A x a125 + B

Solving the two formulas (2) and (3) formulated as described above, it is possible to determine a32, a125, and a134a.

Then, by the formulas a32 = A x a125 + B and a32 + a125 + a134a = 1, if the value of one of the three is already known types of components of the cyclic composition, the values of the other components can also be determined from these formulas Therefore, a32 is also shown as a value representative of the cyclic composition.

In addition, although the embodiment is used in this embodiment mixed non-azeotropic refrigerant of three types, in a Non-azeotropic refrigerant of two types mixed composition Cyclic is determined only by the remaining formula other than the experimental formula in the equilibrium composition gas-liquid

Next, the composition will be described in the refrigeration apparatus 81. The refrigerant compositions circulating in the refrigeration cycle, including the composition of the gas refrigerant inside the accumulator 6, they are identical put that the refrigerant is circulating in the refrigeration cycle. Therefore, during heating, the refrigerant gas in the accumulator 6, the refrigerant gas discharged from the compressor 1, and the coolant at the outlet of the heat exchanger Indoor unit 3 are identical in terms of their compositions. Meanwhile, also during cooling, the refrigerant gas in the accumulator 6, the refrigerant gas discharged from the compressor 1, and the coolant at the outlet of the outdoor unit heat exchanger 5 are identical in terms of his compositions. On the other hand, if you consider the coolant gas and coolant in the accumulator 6, the gas-liquid equilibrium ratio exists in the accumulator 6. When the gas-liquid balance exists in the non-azeotropic refrigerant, the gas is a refrigerant containing larger amounts of components of boil lower than liquid. Therefore, the refrigerant gas in the accumulator 6 results in a refrigerant in which contain low boiling refrigerants R.32 and R.125 in larger quantities than the coolant. On the other hand, the coolant in the accumulator 6 results in a coolant in which the high boiling refrigerant R.134a is contained in a greater amount than the gas refrigerant. Total refrigerant in refrigeration apparatus 81 is a refrigerant in which add the refrigerant circulating in the refrigeration apparatus 81 and the coolant in the accumulator 6, and therefore the composition of the added refrigerant is identical to the R.407C refrigerant composition charged. Therefore in a case in which the liquid refrigerant is present in the accumulator 6, the composition of the refrigerant circulating in the refrigeration cycle depicted in figure 1, including the composition of the gas refrigerant in the accumulator 6, a refrigerant in which the boiling refrigerants low R.32 and R.125 are contained in larger quantities than the refrigerant charged while the composition of the coolant in the accumulator 6 results in a refrigerant in which the refrigerant of high boiling R.134a is contained in a greater amount than the R.407C refrigerant composition charged. In addition, in a case in that the coolant is not present in the accumulator 6, the composition of the refrigerant circulating in the apparatus of cooling 81 in figure 1 is the same composition as the from R.407C.

Next, a method of control the operation of the speed output device Rotary fan / compressor frequency 17 to control the condensation temperature and the evaporation temperature of the refrigerant circuit according to the first embodiment of the present invention During the operation of the device cooling, the rotary speed output device of the compressor fan / frequency 17 determines an average value of gas saturation temperature and saturation temperature of liquid at a detected value P16 based on the detected P16 value by the first pressure detector 16, a calculation made by the composition calculator 14, and the detected value a of the cyclic composition, and this average value is established as the condensing temperature In addition, the output device of rotary fan-frequency speed of compressor 17 determines an average temperature value of gas saturation and liquid saturation temperature at a value detected P13 based on the value P13 detected by the second pressure detector 13 and the detected value a of the composition cyclic, and this average value is set as the temperature of evaporation. However, the T12 value of the second detector of temperature 12 can be set as the temperature of evaporation. The rotational speed output device of the compressor fan / frequency 17 calculates and compares the condensing temperature and evaporation temperature as well determined with the respective target values incorporated, and sends the rotational speed of the fan 7 and the frequency of the compressor 1 to fan 7 and compressor 1, respectively, of so that the respective values will be set to the values White.

As a specific example of controlling the rotary speed output device compressor fan / frequency 17, control is carried out by a combination of an increase in the temperature of condensation and a decrease in evaporation temperature due to an increase in the frequency (an increase in the speed of rotation) of compressor 1, or a decrease in the temperature of condensation and an increase in evaporation temperature due to a decrease in frequency (a decrease in speed of rotation) of compressor 1, as well as a decrease in condensing temperature during cooling and an increase in evaporation temperature during heating due to a increased rotation speed (an increase in air volume of the fan) of the fan 7, or an increase in the temperature of condensation during cooling and a decrease in evaporation temperature during heating due to a decrease in fan rotation speed 7.

In addition, as for the control to change the rotation speed by the frequency of compressor 1, the capacity can be controlled using a compressor provided with called capacity control mechanism.

In addition, although, in the embodiment described above, the fan / fre- quency rotary speed output device
The amount of the compressor 17 determines the condensation temperature and the evaporation temperature, devices for determining them respectively or a device for determining them can be provided separately, and the condensation temperature and evaporation temperature can be determined by these devices and can be transferred to the rotary fan speed output device / compressor frequency 17.

In addition, in the case of a unit that performs operation at a fixed frequency and with a fixed capacity of the indoor unit in which the temperature changes of condensation or evaporation temperature are not large, it can provide for a type of control, such as fan control only or compressor control only.

Second realization

In the first embodiment of the present invention, control is performed to set the temperature of condensation and evaporation temperature at fixed levels for ensure a fixed capacity of the refrigeration apparatus and of air conditioning; however, if the composition changes cyclic refrigerant, condensing temperature and evaporation temperature are fixed, but the pressure of condensation and evaporation pressure change. For this reason, the pressure difference at the inlet and outlet of the first throttle device 4 changes, so that the speed of flow in the refrigerant circuit and subcooling in the input of the first throttling device 4 in the Coolant flow direction also change. Thus, the opening of the first throttling device being fixed 4, the flow rate in the refrigerant circuit and the subcooling at the input of the first device choke 4 in the direction of coolant flow undergo change due to the change in the cyclic composition of the refrigerant, so that an optimum range of the opening of the first throttling device 4 changes due to the cyclic composition of the refrigerant. Therefore, in a second embodiment of the present invention, said minimum opening of the first throttling device 4 which makes it possible to fix the flow rate in the refrigerant circuit and the subcooling at the input of the first device choke 4 in the direction of flow of the refrigerant is can set using the pressure difference across the first throttling device 4 that changes by changing the cyclic composition of the refrigerant.

Figure 3 illustrates a refrigeration apparatus 82 which is an example of the refrigeration apparatus and of air conditioning using a non-refrigerant azeotropic according to the present invention. In this device of cooling 82, variable capacity compressor 1, valve four-way 2, the indoor unit heat exchanger 3 that is the use side heat exchanger, the first device of throttling 4, the outdoor unit heat exchanger 5 that It is the heat exchanger unit side heat exchanger, the accumulator 6, and compressor 1 are connected in series in this order through the tubes, thus forming the refrigerant circuit. At the same time, through a change made by the valve four-way, compressor 1, four-way valve 2, the outdoor unit heat exchanger, the first device throttling 4, the indoor unit heat exchanger 3, the accumulator 6, and compressor 1 are connected in series in this order by the tubes, thus forming another circuit of refrigerant. In addition, the refrigeration apparatus 82 is provided of the cyclic composition detector device 15, the first pressure detector 16 disposed in the discharge tube of the compressor 1, the second pressure detector 13 disposed in the tube suction of compressor 1, a fifth temperature detector 35 and a sixth temperature detector 36 arranged respectively before and after the first throttling device 4, and a seventh temperature detector 37 for the heat exchanger indoor unit to detect the ambient temperature. In addition, the outdoor unit heat exchanger is provided with the fan variable capacity 7. The cooling device 82 is also provided with the rotary speed output device of the compressor fan / frequency 17, which are means of fan / compressor capacity control to send the rotational speed of this fan 7 and the frequency of compressor 1, as well as a minimum opening calculator throttling device 18 to calculate and send a minimum opening of the first throttling device 4 and a subcooling calculator 38 to calculate and send the degree of subcooling before and after the first device throttling 4. The device shown in figure 3 is similar to that of the first embodiment of the present invention a except that the minimum opening calculator has been provided of the throttling device 18, the fifth detector of temperature 35, the sixth temperature detector 36, the seventh temperature detector 37, and subcooling calculator 38, so that a description of the components will be omitted Similar.

Next, the calculator of subcooling 38 and the minimum opening calculator of the throttling device 18. During the operation of cooling, subcooling calculator 38 calculates a temperature difference in which the value of the fifth detector of temperature 35 is subtracted from the condensation temperature to the value P16 of the first pressure detector 16 and the cyclic composition of refrigerant to, while, during the heating operation, subcooling calculator 38 calculates a difference of temperature at which the value of the sixth temperature detector 36 the condensation temperature is subtracted from the first P16 value pressure detector 16 and the cyclic refrigerant composition a, therefore calculating the subcooling in the first device of throttling 4 to control the opening of the first throttling device 4 so that subcooling it will be set to a default white value. However, if the first throttling device 4 is controlled by the subcooling calculator 38, there are cases in which, although can ensure subcooling, coolant flow It is small, resulting in a capacity deficiency. By therefore, you must specify a minimum opening for the first throttling device 4. For this reason, the P16 value of the first pressure detector 16, the P13 of the second detector of pressure 13, and the cyclic refrigerant composition a are introduced in the minimum opening calculator of the device throttling 18 to send a minimum device opening of throttling X using the formulas listed to then, and therefore control is done to not allow the opening of the first throttling device 4 is less than said X, thus preventing the appearance of a deficiency in coolant flow due to excessive throttling. TO know, the device's minimum opening output device choke 18 receives an order about the opening of the first throttle device 4 of the calculator subcooling 38, and if this opening order is greater than X, the output device minimum opening device throttling 18 sends to the first throttling device 4 the value of the opening order determined by the calculator subcooling 38, while if the opening order is greater or same as X, the minimum opening output device of the throttling device 18 sends to the first device of Strangulation 4 an order in which the value is set to X. Through the control that takes into account the composition cyclic refrigerant a, an optimal opening can be guaranteed of the first throttling device 4 that does not excessively small amount of refrigerant and makes possible guarantee subcooling.

(4) During heating: X = K \ cdot (Tc - T37) / \ surd \ (P16 - P13)

(5) During cooling: X = K \ cdot (T37 - Te) / \ surd \ (P16 - P13)

Here, K is a minimum opening coefficient of the throttling device, Tc is the temperature of condensation calculated from P16 and a, Te is the temperature of evaporation calculated from P13 and a, and T37 is the temperature indoor unit heat exchanger environment detected by the seventh temperature detector 37.

The above formulas (4) and (5) are derived as shown below. If the amount of thermal exchange between the indoor unit heat exchanger 3 and the refrigerant flowing through the heat exchanger of indoor unit 3 is Q1, the amount of heat exchange between the indoor unit heat exchanger 3 and side air indoor unit is Q2, and the opening of the first device of strangulation 4 is Xa, we have

(6) Q1 \ \ infty \ \ cdot \ surd \ (P16 - P13)

(7) During heating: Q2 \ \ infty \ (Tc - T37)

(8) During cooling: Q2 \ \ infty \ (T37 - Tea)

In addition, since Q1 = Q2, with certain the following formulas:

(9) During heating: Xa \ cdot \ surd \ (P16 - P13) \ \ infty \ (Tc - T37)

(10) During cooling: Xa \ cdot \ surd \ (P16 - P13) \ \ infty \ (T37 - Tea)

As for the formulas on X to which the coolant of a minimum level in terms of flow, it is possible formulate (4) and (5) based on formulas (9) and (10).

In addition, in the control to establish the evaporation temperature Te and the condensation temperature Tc a fixed levels, since \ surd (P16 - P13) is a function of a, K can be set based on a, that is, K (a), as follows:

(11) During heating: X = K (a) \ cdot (Tc - T37)

(12) During cooling: X = K (a) \ cdot (T37 - Tea)

In addition, although in this embodiment the calculator subcooling 38 determines the condensation temperature, it you can separately provide a device for determining condensing temperature to send the temperature of condensation to the subcooling calculator 38. Also of form alternatively, an adapted device can be provided separately to receive both the opening order of the calculator from subcooling 38 as an outlet over the minimum opening calculated by the minimum opening calculator of the device choke 18, compare them, and send the opening order or the minimum opening calculated to the first throttling device Four.

Figure 4 illustrates a refrigeration apparatus 83 which is an example of the refrigeration apparatus and of air conditioning using a non-refrigerant azeotropic according to the present invention. In this device of cooling 83, the compressor 1, the four-way valve 2, the indoor unit heat exchanger 3 which is the use side heat exchanger, the first device throttling 4, the outdoor unit heat exchanger 5 that It is the heat exchanger unit side heat exchanger, the accumulator 6, and compressor 1 are connected in series in this order through the tubes, thus forming the refrigerant circuit. At the same time, through a change made by the valve four-way, compressor 1, four-way valve 2, the outdoor unit heat exchanger 5, the first device throttling 4, the indoor unit heat exchanger 3, the accumulator 6, and compressor 1 are connected in series in this order by the tubes, thus forming another circuit of refrigerant. In addition, the cooling apparatus 83 is provided of the cyclic composition detector device 15, the first pressure detector 16 disposed in the discharge tube of the compressor 1, and the second pressure detector 13 arranged in the compressor suction tube 1. In addition, the heat exchanger outdoor unit is provided with fan 7, and the speed Rotational fan 7 and compressor frequency 1 are calculated and changed by the speed output device Rotary fan / compressor frequency 17. The appliance cooling 83 is also provided with a bypass tube, which connects the discharge tube of compressor 1 and accumulator 6 and in which an opening / closing valve 19 and a second pressure reducing device 20 are connected in series as well as a first opening / closing output device 21 for send an order about the opening and closing of the valve opening / closing 19 based on the value of the second pressure detector 13. The device shown in Figure 4 is similar to that of the first embodiment of the present invention except for the tube bypass with the opening / closing valve 19 and the second pressure reducing device 20 connected in series and the first opening / closing output device 21, so that it omit a description of similar components.

Next, the control and the operation according to the third embodiment of the present invention. The first opening / closing output device 21 sends to the opening / closing valve 19 a signal to open the valve opening / closing 19 when, during the operation of compressor 1, the value of the second pressure detector 13 has become a value default at which the suction pressure is considered excessively low, for example, less than 1 kgf / cm2G, while the first opening / closing output device 21 sends a signal to close the opening / closing valve 19 opening / closing valve 19 when the value of the second detector pressure 13 has become greater than or equal to 1 kgf / cm2G. The opening / closing valve 19 opens or closes in response to this signal. Through this control, the gas at high temperature and high pressure in the discharge portion of compressor 1 is subjected to pressure reduction by the second reducing device pressure 20, and then supplied to the inside of the accumulator. Then, the refrigerant containing a large amount evaporates of the low boiling component R.32 in the refrigerant R.407C accumulated in the accumulator, and the refrigerant is supplied to the compressor 1. As for this refrigerant containing a large amount of R.32, its saturation pressure at the same temperature is higher than that of the refrigerant that has the components of R.407C. For this reason, it is possible to increase the pressure in the suction portion of compressor 1 by two effects that the refrigerant can be supplied to compressor 1 and that the Refrigerant supplied is a refrigerant that has high pressure saturation

In addition, as shown in Figure 5, if the contact point between the accumulator 6 and the tube in which the opening / closing valve 19 and the second reducing device pressure 20 are connected in series is arranged in such a way that a distal end portion of the bypass tube bends laterally, and opens in the lateral direction instead of opening in the upward direction, it is difficult for the refrigerant liquid present in the accumulator enters the bypass tube including the opening / closing valve 19 and the second pressure reducing device 20, and the refrigerant gas at high temperature can easily be supplied to the refrigerant accumulated in the accumulator. As a result, you can make the coolant accumulated in the accumulator form foam, making possible therefore allow the accumulated refrigerant to evaporate efficiently.

By the way, although one end of the tube bypass is connected to the accumulator 6, the bypass tube is you can connect to the tube on the side located up or down of the accumulator 6 to the extent that the tube is the tube of compressor suction.

Quarter realization

In terms of the saturation pressure of R.22 and R.407C in case the temperature is the same, the temperature saturation of R.407C is greater than 2 kgf / cm2 or more, at temperature of 50 ° C the pressure in the discharge portion of the Compressor 1 is higher in the case of R.407C. Therefore, In a third embodiment of the present invention, the valve opening / closing 19 opens when the value of the second detector of pressure 13 is less than a fixed value to raise the pressure in the suction portion of compressor 1, but the pressure in the portion Compressor 1 discharge can be decreased by opening the valve opening / closing 19 to protect the compressor 1.

Figure 6 illustrates a refrigeration apparatus 84 which is an example of the refrigeration apparatus and of air conditioning using a non-refrigerant azeotropic according to the present invention. In this device of cooling 84, the compressor 1, the four-way valve 2, the indoor unit heat exchanger 3 which is the use side heat exchanger, the first device throttling 4, the outdoor unit heat exchanger 5 that It is the heat exchanger unit side heat exchanger, the accumulator 6, and compressor 1 are connected in series in this order through the tubes, thus forming the refrigerant circuit. At the same time, through a change made by the valve four-way, compressor 1, four-way valve 2, the outdoor unit heat exchanger 5, the first device throttling 4, the indoor unit heat exchanger 3, the accumulator 6, and compressor 1 are connected in series in this order by the tubes, thus forming another circuit of refrigerant. In addition, the refrigeration apparatus 84 is provided of the cyclic composition detector device 15, the first pressure detector 16 disposed in the discharge tube of the compressor 1, and the second pressure detector 13 arranged in the compressor suction tube 1. In addition, the heat exchanger outdoor unit is provided with fan 7, and the speed Rotational fan 7 and compressor frequency 1 are calculated and changed by the speed output device Rotary fan / compressor frequency 17. The appliance cooling 84 is further provided with the bypass tube, which connect the discharge pipe of compressor 1 and accumulator 6 and in which the opening / closing valve 19 and the second device pressure reducer 20 are connected in series, as well as a second opening / closing output device 22 to send a order about the opening and closing of the valve opening / closing 19 based on the value of the first pressure detector 16. The device shown in Figure 6 is similar to that of the first embodiment of the present invention except for the tube bypass with the opening / closing valve 19 and the second pressure reducing device 20 connected in series and the second opening / closing output device 22, so that it omit a description of similar components.

Next, the control and the operation according to the fourth embodiment of the present invention. The second opening / closing output device 22 sends to the opening / closing valve 19 a signal to close the valve opening / closing 19 when, during the operation of compressor 1, the value of the first pressure detector 16 has become a predetermined pressure determined taking into account the unit pressure resistance, for example, less than 27 kgf / cm2 G, while the second output device of opening / closing 22 sends to the opening / closing valve 19 a signal to open the opening / closing valve 19 when the value of the first pressure detector 16 has become greater than or equal to 27 kgf / cm2 G. The opening / closing valve 19 opens or closes in response to this signal. Through this control, the part of the gas a high temperature and high pressure in the discharge portion of the compressor 1 flows through the tube in which the valve opening / closing 19 and the second pressure reducing device 20 they are connected in series, and bypass the main line to be supplied to the accumulator, so as to reduce the pressure in the discharge portion of the compressor 1.

In addition, in another embodiment of the present invention, the opening / closing pressure of the valve opening / closing 19 can be set depending on the composition cyclic refrigerant to taking into account the fact that the saturation pressure changes due to the cyclic composition of refrigerant. Namely, the opening / closing pressure can be made large or small by the relative magnitude of the pressure of saturation, and it is possible to avoid a decrease in capacity due to a deficiency of the amount of refrigerant flowing in the main circuit, particularly in the case of the composition whose saturation pressure is large.

As the refrigerant in this embodiment, it is effective a refrigerant that is an HFC based refrigerant and whose saturation pressure is higher than that of R.22 at the same temperature.

Fifth realization

Since the R.407C refrigerant has a low dielectric constant compared to refrigerant R.22, in case the compressor starts up under vacuum, corona discharge tends to occur in the case of R.407C (short circuit of an engine section and the like), and tends to Compressor damage due to this phenomenon will occur.

Figure 7 illustrates a refrigeration apparatus 85 which is an example of the refrigeration apparatus and of air conditioning using a non-refrigerant azeotropic according to the present invention. In this device of cooling the compressor 1, the four-way valve 2, the indoor unit heat exchanger 3 which is the use side heat exchanger, the first device throttling 4, the outdoor unit heat exchanger 5 that It is the heat exchanger unit side heat exchanger, the accumulator 6, and compressor 1 are connected in series in this order through the tubes, thus forming the refrigerant circuit. At the same time, through a change made by the valve four-way, compressor 1, four-way valve 2, the outdoor unit heat exchanger 5, the first device throttling 4, the indoor unit heat exchanger 3, the accumulator 6, and compressor 1 are connected in series in this order by the tubes, thus forming another circuit of refrigerant. In addition, the refrigeration apparatus 85 is provided of the cyclic composition detector device 15, the first pressure detector 16 disposed in the discharge tube of the compressor 1, and the second pressure detector 13 arranged in the compressor suction tube 1. In addition, the heat exchanger outdoor unit is provided with fan 7, and the speed Rotational fan 7 and compressor frequency 1 are calculated and changed by the speed output device Rotary fan / compressor frequency 17. The appliance cooling 85 is further provided with a first device of compressor stop output 23 to send a signal to stop compressor 1 in response to the value of the second pressure detector  13. The device shown in Figure 7 is similar to that of the first embodiment of the present invention except for the first compressor stop output device 23, so that it omit a description of similar components.

Next, the control and the operation according to the fifth embodiment of the present invention. When the value of the second pressure detector 13 has reached be, for example, 0 kgf / cm2 G or less, which is the level of pressure indicating that the compressor will perform vacuum operation, the first compressor stop output device 23 sends a signal to stop the operation of compressor 1, in response to that the compressor is stopped 1. Consequently, no damage occurs in the compressor due to corona discharge, which tends to occur with R.407C.

As the refrigerant in this embodiment, it is effective a refrigerant that is an HFC based refrigerant and with the which is more prone to corona discharge than with R.22.

Sixth realization

If the compressor discharge temperature is high, the sludge that exerts adverse effects on the refrigerant circuit, such as device blockage of strangulation, and occur frequently in cases where that an ester oil or an ether oil is used as the oil of refrigerating machine

Therefore, in a sixth embodiment of the In the present invention, control is carried out to prevent the compressor discharge temperature reaches a fixed value or plus.

Figure 8 illustrates a refrigeration apparatus 86 which is an example of the refrigeration apparatus and of air conditioning using a non-refrigerant azeotropic according to the present invention. In this device of cooling 86, compressor 1, four-way valve 2, the indoor unit heat exchanger 3 which is the use side heat exchanger, the first device throttling 4, the outdoor unit heat exchanger 5 that It is the heat exchanger unit side heat exchanger, the accumulator 6, and compressor 1 are connected in series in this order through the tubes, thus forming the refrigerant circuit. At the same time, through a change made by the valve four-way, compressor 1, four-way valve 2, the outdoor unit heat exchanger 5, the first device throttling 4, the indoor unit heat exchanger 3, the accumulator 6, and compressor 1 are connected in series in this order by the tubes, thus forming another circuit of refrigerant. In addition, the refrigeration apparatus 86 is provided of the cyclic composition detector device 15, the first pressure detector 16 and a third temperature detector 24 arranged both in the discharge tube of the compressor 1, and the second pressure detector 13 disposed in the suction tube of the compressor 1. In addition, the outdoor unit heat exchanger it is provided with fan 7, and the rotational speed of the fan 7 and the frequency of compressor 1 are calculated and changed by the rotary speed output device of the compressor fan / frequency 17. The cooling device 86 is also provided with the bypass tube, which connects the discharge tube of compressor 1 and accumulator 6 and in which the opening / closing valve 19 and the second reducing device Pressure 20 are connected in series. In addition, the apparatus of cooling 86 has a third output device of opening / closing 25 to send an order about the opening and the opening / closing valve closure 19 based on the value of the third pressure detector 24. The device represented in the Figure 8 is similar to that of the first embodiment of the present invention except for the bypass tube with the valve opening / closing 19 and the second pressure reducing device 20 connected in series, the third temperature detector 24, and the third opening / closing output device 25, so that it  omit a description of similar components.

Next, the control and the operation according to the sixth embodiment of the present invention. The third opening / closing output device 25 sends to the opening / closing valve 19 a signal to close the valve opening / closing 19 when, during the operation of compressor 1, the value of the third temperature detector 24 has become, by example, below 120 ° C, while the third device opening / closing output 25 sends to the opening / closing valve 19 a signal to open the opening / closing valve 19 when the value of the third temperature detector 24 has become higher or equal to 120 ° C. The opening / closing valve 19 opens or closes in response to this signal. Through this control, part of the gas a high temperature and high pressure in the discharge portion of the compressor 1 flows through the tube in which the valve opening / closing 19 and the second pressure reducing device 20 they are connected in series, and bypass the main line to be supplied to the accumulator, so that the pressure and temperature in the discharge portion of compressor 1, and sludge appearance decreases.

As an alternative method, the operation of the compressor can be stopped when the value of the third detector of temperature 24 has become greater than or equal to 120 ° C during the compressor operation 1.

Seventh realization

If the degree of superheat in the portion Compressor discharge is low during the operation of the compressor, the compressor compresses the coolant, and there is a possibility of damaging the compressor. Therefore, in a seventh embodiment of the present invention, the degree of superheating in the discharge portion of the compressor it is calculated from the values of the pressure detector and the temperature detector in the Compressor discharge tube and the value of the cyclic composition of refrigerant so that they provide control to prevent this degree of superheat falls below a value predetermined.

Figure 9 illustrates a refrigeration apparatus 87 which is an example of the refrigeration apparatus and of air conditioning using a non-refrigerant azeotropic according to the present invention. In this device of cooling 87, the compressor 1, the four-way valve 2, the indoor unit heat exchanger 3 which is the use side heat exchanger, the first device throttling 4, the outdoor unit heat exchanger 5 that It is the heat exchanger unit side heat exchanger, the accumulator 6, and compressor 1 are connected in series in this order through the tubes, thus forming the refrigerant circuit. At the same time, through a change made by the valve four-way, compressor 1, four-way valve 2, the outdoor unit heat exchanger 5, the first device throttling 4, the indoor unit heat exchanger 3, the accumulator 6, and compressor 1 are connected in series in this order by the tubes, thus forming another circuit of refrigerant. In addition, the cooling apparatus 87 is provided of the cyclic composition detector device 15, the first pressure detector 16 and the third temperature detector 24 arranged both in the discharge tube of the compressor 1, and the second pressure detector 13 disposed in the suction tube of the compressor 1. In addition, the outdoor unit heat exchanger it is provided with fan 7, and the rotational speed of the fan 7 and the frequency of compressor 1 are calculated and changed by the rotary speed output device of the compressor fan / frequency 17. The cooling device 87 is also provided with a second output device of compressor stop 26 to calculate a TdSH value that is the difference between the value of the third temperature detector 24 and the gas saturation temperature of the first pressure detector 16 (the latter being the temperature when all the refrigerant liquid has become the refrigerant gas, and the values of the cyclic composition of refrigerant a and the first pressure detector 16), and to send a signal to stop the compressor 1 based on the TdSH value. The device represented in the Figure 9 is similar to that of the first embodiment of the present invention except for the third temperature detector 24 and the second compressor stop output device 26, so that a description of similar components will be omitted.

Next, the control and the operation according to the seventh embodiment of the present invention. During the operation of compressor 1, the second device of compressor stop output 26 calculates the TdSH value which is the difference between the value of the third temperature detector 24 and the gas saturation temperature of the first pressure detector 16 (the latter being the temperature when all the refrigerant liquid has become the refrigerant gas, and the values of the cyclic composition of refrigerant a and the first pressure detector 16). When the state in which this TdSH value is less than or equal to a predetermined value, in whose range it is not you can get a predetermined degree of superheating, it is that is, it is considered that there is liquid compression, for example, 20 degrees, continues for a predetermined period of time, by for example, for 10 minutes, the operation of compressor 1 is stopped, thereby preventing damage to the compressor.

In addition, as an alternative method, an apparatus of refrigeration, as shown in figure 10, can be control as shown in figure 11. Figure 10 illustrates a refrigeration apparatus 88 which is an example of the apparatus of cooling and air conditioning that uses a non azeotropic refrigerant according to the present invention. In this cooling device 88, compressor 1, valve four lanes 2, the indoor unit heat exchanger 3 which is the use side heat exchanger, the first device throttling 4, the outdoor unit heat exchanger 5 that It is the heat exchanger unit side heat exchanger, the accumulator 6, and compressor 1 are connected in series in this order through the tubes, thus forming the refrigerant circuit. At the same time, through a change made by the valve four-way, compressor 1, four-way valve 2, the outdoor unit heat exchanger 5, the first device throttling 4, the indoor unit heat exchanger 3, the accumulator 6, and compressor 1 are connected in series in this order by the tubes, thus forming another circuit of refrigerant. In addition, the cooling apparatus 88 is provided of the cyclic composition detector device 15, the first pressure detector 16 and the third temperature detector 24 arranged both in the discharge tube of the compressor 1, and the second pressure detector 13 disposed in the suction tube of the compressor 1. In addition, the outdoor unit heat exchanger it is provided with fan 7, and the rotational speed of the fan 7 and the frequency of compressor 1 are calculated and changed by the rotary speed output device of the compressor fan / frequency 17. The cooling device 88 is further provided with a reduction output device opening of the throttling device 27 to calculate the TdSH value which is the difference between the value of the third detector of temperature 24 and the gas saturation temperature of the first pressure detector 16 (the latter being the temperature when all the liquid refrigerant has become the refrigerant gas, and the values of the cyclic composition of refrigerant a and the first pressure detector 16), and to send a signal to reduce the opening of the first device of throttling 4 based on the TdSH value. The device depicted in figure 10 is similar to that of the first embodiment of the present invention with the exception of the third detector of temperature 24 and the reduction output device of throttle device opening 27, so that it omit a description of similar components.

Next, the control and the operation according to the modification described above of the seventh embodiment of the present invention. In terms of the content of control in figure 11, during the operation of compressor 1, the aperture reduction output device of the device throttling 27 calculates the TdSH value which is the difference between the value of the third temperature detector 24 and the saturation gas temperature of the first pressure detector 16 (the latter being the temperature when all the refrigerant liquid has become the gas refrigerant, and they are introduced the values of the cyclic composition of refrigerant a and the first pressure detector 16) (step 1). The output device of throttle device aperture reduction 27 determines whether the state in which this TdSH value is less than or equal at a predetermined value, in whose range you cannot obtain a predetermined degree of superheating, that is, it is considered that there is liquid compression, for example, 20 degrees, continues or not for 10 minutes (step 2). If the state in which the value is less than or equal to 20 degrees continues for 10 minutes, the opening of the first throttling device 4 closes a predetermined amount, for example, 10 pulses (step 3). After, the first throttling device 4 closes until TdSH  be greater than 20 degrees. When the first device is closed strangulation 4, you can increase the difference between the discharge pressure and compressor suction pressure, and it increases the power supplied from the compressor to refrigerant, thereby facilitating gasification of the refrigerant.

Eighth realization

If the machine oil temperature refrigerant in the compressor is high, the oil lubricity of refrigerant machine decreases, and there is a possibility of damaging the compressor With the refrigerant circuit according to the sixth embodiment of the present invention, however, is impossible accurately know the machine oil temperature refrigerant (in particular in the case of R.407C, an error about the cyclic composition of the refrigerant affects the error in the refrigerant machine oil temperature detection, it is harder to know the machine oil temperature refrigerant than in the case of R.22). Therefore, in a eighth embodiment of the present invention, a detector is provided of temperature in a position where the temperature can be measured of the refrigerating machine oil in the compressor body, and it performs control to protect the compressor, ensuring that the operation will not be performed for a long time when the temperature of this temperature detector is at a fixed level or plus.

Figure 12 illustrates a refrigeration apparatus 89 which is an example of the refrigeration apparatus and of air conditioning using a non-refrigerant azeotropic according to the present invention. In this device of cooling 89, the compressor 1, the four-way valve 2, the indoor unit heat exchanger 3 which is the use side heat exchanger, the first device throttling 4, the outdoor unit heat exchanger 5 that It is the heat exchanger unit side heat exchanger, the accumulator 6, and compressor 1 are connected in series in this order through the tubes, thus forming the refrigerant circuit. At the same time, through a change made by the valve four-way, compressor 1, four-way valve 2, the outdoor unit heat exchanger 5, the first device throttling 4, the indoor unit heat exchanger 3, the accumulator 6, and compressor 1 are connected in series in this order by the tubes, thus forming another circuit of refrigerant. In addition, the refrigeration apparatus 89 is provided of the cyclic composition detector device 15, the first pressure detector 16 disposed in the discharge tube of the compressor 1, a fourth temperature detector 28 arranged in a position where the temperature of the refrigerating machine oil in a lower portion of the body of the compressor 1 may be detected, and the second pressure detector 13 arranged in the tube suction of the compressor 1. In addition, the heat exchanger of outdoor unit is provided with fan 7, and the speed Rotational fan 7 and compressor frequency 1 are calculated and changed by the speed output device Rotary fan / compressor frequency 17. The appliance cooling 89 is also provided with a third device of compressor stop output 29 to send a signal to stop compressor 1 based on the value of the fourth temperature detector 28. The device depicted in Figure 12 is similar to that of the first embodiment of the present invention with the exception of the fourth temperature detector 28 and the third output device of compressor stop 29, so that a description of Similar components

Next, the control and the operation according to the eighth embodiment of the present invention. During the operation of compressor 1, the third device of Compressor stop output 29 detects that the room value temperature detector 22 has reached a predetermined value, for example, 100 ° C, and that this state has continued for 60 minutes In that case, the third stop output device of compressor 29 sends a signal to stop the operation of the compressor 1, so that compressor 1 stops.

Ninth realization

If machine oil concentration refrigerant in the compressor is low, the oil lubricity of refrigerant machine decreases, and there is a possibility of damaging the compressor Therefore, in a ninth embodiment of the present invention, machine oil concentration refrigerant in the compressor body is represented as the difference between the temperature of the refrigerating machine oil and the saturation temperature of the refrigerant gas at the pressure of suction side of the compressor, and control is performed to protect the compressor, ensuring that the operation is not will take a long time when this value is at a fixed level or more.

Figure 13 illustrates a refrigeration apparatus 90 which is an example of the refrigeration apparatus and of air conditioning using a non-refrigerant azeotropic according to the present invention. In this device of cooling the compressor 1, the four-way valve 2, the indoor unit heat exchanger 3 which is the use side heat exchanger, the first device throttling 4, the outdoor unit heat exchanger 5 that It is the heat exchanger unit side heat exchanger, the accumulator 6, and compressor 1 are connected in series in this order through the tubes, thus forming the refrigerant circuit. At the same time, through a change made by the valve four-way, compressor 1, four-way valve 2, the outdoor unit heat exchanger 5, the first device throttling 4, the indoor unit heat exchanger 3, the accumulator 6, and compressor 1 are connected in series in this order by the tubes, thus forming another circuit of refrigerant. In addition, the cooling apparatus 90 is provided of the cyclic composition detector device 15, the first pressure detector 16 disposed in the discharge tube of the compressor 1, a fourth temperature detector 28 arranged in a position where the temperature of the refrigerating machine oil in a lower portion of the body of the compressor 1 may be detected, and the second pressure detector 13 arranged in the tube suction of the compressor 1. In addition, the heat exchanger of outdoor unit 5 is provided with fan 7, and the speed Rotational fan 7 and compressor frequency 1 are calculated and changed by the speed output device Rotary fan / compressor frequency 17. The appliance cooling 90 is also provided with a fourth device of compressor stop output 30 to calculate a TsSH value that is the difference between the value of the fourth temperature detector 28 and  the gas saturation temperature of the second detector of pressure 13 (the latter being the temperature when all the liquid refrigerant has become the gas refrigerant, and it enter the values of the cyclic refrigerant composition a and the second pressure detector 13), and to send a signal to stop the operation of compressor 1 based on the TsSH value. The device shown in figure 13 is similar to that of the first embodiment of the present invention except for the third temperature detector 28 and the fourth output device of compressor stop 30, so that a description of Similar components

Next, the control and the operation according to the ninth embodiment of the present invention. During the operation of compressor 1, the fourth device of Compressor stop output 30 detects that the TsSH value which is the difference between the value of the fourth temperature detector 28 and the gas saturation temperature of the second pressure detector 13 (the latter being the temperature when all the refrigerant liquid has become the gas refrigerant, and they are introduced the values of the cyclic composition of refrigerant a and the second pressure detector 13) has become less than or equal to a default value, for example, 10 degrees or less, which indicates that the coolant is mixed in the coolant machine oil in a great deal, and that this state has continued for 60 minutes In that case, the fourth stop output device of compressor 30 sends a signal to stop the operation of the compressor 1, so that compressor 1 stops.

Tenth realization

Figure 14 illustrates a refrigeration apparatus 91 which is an example of the refrigeration apparatus and of air conditioning using a non-refrigerant azeotropic according to the present invention. In this device of cooling the compressor 1, the four-way valve 2, the indoor unit heat exchanger 3 which is the use side heat exchanger, the first device throttling 4, the outdoor unit heat exchanger 5 that It is the heat exchanger unit side heat exchanger, the accumulator 6, and compressor 1 are connected in series in this order through the tubes, thus forming the refrigerant circuit. At the same time, through a change made by the valve four-way, compressor 1, four-way valve 2, the outdoor unit heat exchanger 5, the first device throttling 4, the indoor unit heat exchanger 3, the accumulator 6, and compressor 1 are connected in series in this order by the tubes, thus forming another circuit of refrigerant. In addition, the refrigeration apparatus 91 is provided of the cyclic composition detector device 15, the first pressure detector 16 disposed in the discharge tube of the compressor 1, and the second pressure detector 13 arranged in the compressor suction tube 1. In addition, the heat exchanger outdoor unit is provided with fan 7, and the speed Rotational fan 7 and compressor frequency 1 are calculated and changed by the speed output device Rotary fan / compressor frequency 17. The appliance cooling 91 is also provided with a circuit of refrigerant connecting a first fork point 31 located between the heat exchanger 5 and the first device choke 4 and a second fork point 32 located between the four-way valve 2 and the accumulator 6, and in which a second throttling device 33 and a second 34 double tube heat exchanger for exchange thermal with a portion of the tube between the heat exchanger 5 and the first fork point 31 are connected in series by the tube. The first fork point 31, the second point of fork 32, the second throttling device 33, and the second double tube heat exchanger 34 form a device of subcooling. The device shown in Figure 14 is similar to that of the first embodiment of the present invention a exception of the refrigerant circuit that connects the first point of fork 31 located between the heat exchanger 5 and the first throttling device 4 and the second fork point 32 located between the four-way valve 2 and the accumulator 6, and in which the second throttling device 33 and the second double tube heat exchanger 34 to perform thermal exchange with a portion of the tube between the heat exchanger 5 and the first fork point 31 are connected in series by the tube, so that a Description of similar components.

Next, the control and the operation according to the tenth embodiment of the present invention. In the second double tube heat exchanger 34, the refrigerant that has experienced thermal exchange with the heat exchanger of outdoor unit 5 during cooling, experience exchange thermal with the low-pressure two-phase refrigerant subjected to pressure reduction going through the second device throttling of the first fork point, guaranteeing by This is the degree of subcooling. So, in the case of R.407C, the degree of subcooling assumes a value at which the temperature in said place is subtracted from the liquid saturation temperature under pressure at that place, while, in the case of R.22, the degree of subcooling assumes a value at which the temperature in that place it is subtracted from the saturation temperature under the pressure in that place. For this reason, since the degree of subcooling is difficult to guarantee for R.407C, this embodiment of the present invention is effective. Guaranteeing the degree of subcooling, it is possible to avoid the appearance of noise of refrigerant in the unit throttling device inside (first throttling device 4).

Although in the above described embodiments it has been exposed a description with reference mainly to the case of R.407C, the present invention is also valid for R.404A and R.407A, which are non-azeotropic refrigerants, and for R.410A and R410B, which are pseudoazeotropic refrigerants.

Advantages of the invention

As described above, according to the In the present invention, a refrigeration apparatus is provided which uses a non-azeotropic refrigerant and including a circuit of refrigerant in which a compressor of variable capacity, a heat exchanger side heat exchanger, a throttling device, and a side heat exchanger use are connected by tubes, a capacity fan variable for the source unit side heat exchanger heat, a first pressure detector in a discharge tube of the compressor, a second pressure detector in a suction tube of the compressor, and a cyclic composition detector device of refrigerant, characterized by: control means to determine a condensing temperature of the heat exchanger on the side of heat source unit or use side heat exchanger based on a cyclic refrigerant composition detected by the detector device of cyclic composition and a detected pressure by the first pressure detector, or determine a temperature of evaporation of the heat exchanger from the source unit side of heat or use side heat exchanger based on the cyclic refrigerant composition detected by the device cyclic composition detector and a pressure detected by the second pressure detector, and control the compressor capacity and fan capacity for the side heat exchanger heat source unit so that the temperature of condensation and evaporation temperature are set to respective default white values. Therefore, even with the refrigeration apparatus that uses a refrigerant not azeotropic, the operation is performed with the temperature of condensation and evaporation temperature set by taking in Consider the cyclic composition of the refrigerant, so It is possible to guarantee a stable capacity.

According to a second aspect of the present invention, the refrigerant is a refrigerant that is a HFC-based refrigerant and with which it is more prone than produce corona discharge than with R.22, including the cooling a (first) stop output device compressor to stop compressor operation if a pressure detected by the second pressure detector has become less than or equal to a default value that indicates that the Compressor will perform vacuum operation. Therefore with the refrigeration device using R.407C or the like in the which is more prone to compressor damage due to corona discharge under vacuum than in the device using R.22, it is possible to eliminate compressor damage due to discharge in crown.

According to a third aspect of the present invention, the refrigeration apparatus includes a temperature detector in a compressor discharge tube, and a (second) device compressor stop output to calculate a degree of superheating in the compressor discharge tube based on values detected by the first pressure detector, the detector of temperature, and the cyclic composition detector device of refrigerant, and to stop the operation of the compressor if a state in which the degree of superheating is less than or equal to a default has continued for a period of time predetermined. Therefore, even with the device refrigeration using a non-azeotropic refrigerant, it is possible prevent compressor damage due to liquid compression refrigerant in the compressor.

According to a fourth aspect of the present invention, The refrigeration device includes: a temperature detector for detect a temperature of a refrigerating machine oil in the compressor; and a (third) stop output device of compressor to stop compressor operation if a value detected by the temperature detector has become higher or same as a default value, and if the state in which the value detected is greater than or equal to the default value has continued for a predetermined period of time. By consequently, in the refrigeration apparatus that uses a non azeotropic refrigerant, it is possible to avoid compressor damage due to excessive superheating of the compressor detecting the excessive superheating of the compressor that is difficult to detect on the discharge side of the compressor.

According to a fifth aspect of the present invention, the refrigeration apparatus includes a (fourth) device compressor stop output to stop compressor operation if a difference between a temperature of a machine oil refrigerant detected by a temperature detector in the compressor and a gas saturation temperature at a pressure detected by the second pressure detector with a composition of the refrigerant detected by the detection device of cyclic composition has become less than or equal to a value default, and if this status has continued for a period Default time. Therefore, even in the apparatus of  refrigeration that uses a non-azeotropic refrigerant, is possible to detect excessive superheating of the liquid refrigerant, so that it is possible to avoid compressor damage produced by a decrease in machine oil lubricity  refrigerant due to excessive superheating of the liquid refrigerant.

Claims (5)

1. A refrigeration appliance that uses a non azeotropic refrigerant and including: a refrigerant circuit in which a variable capacity compressor (1), a side heat exchanger of heat source unit (5), a throttling device (4), and a use side heat exchanger (3) are connected by tubes; a variable capacity fan (7) for the heat exchanger unit side heat exchanger (5); a first pressure detector (16) in a tube of compressor discharge (1); a second pressure detector (13) in a tube of compressor suction (1); and a detector device of cyclic refrigerant composition (15); characterized by control means (17) for determining a condensation temperature of the heat exchanger side-side heat exchanger (5) or the use-side heat exchanger (3) based on a cyclic refrigerant composition detected by the sensing device of cyclic composition (15) and a pressure detected by the first pressure detector (16), or determining an evaporation temperature of the heat source unit side heat exchanger (5) or the use side heat exchanger (3) in based on the cyclic refrigerant composition detected by said cyclic composition detector device (15) and a pressure detected by the second pressure detector (13), and controlling the capacity of the compressor (1) and the capacity of the fan (7) of so that the condensation temperature and evaporation temperature are set to respective predetermined target values. 2. A refrigerated apparatus as claimed in claim 1, which uses as the refrigerant a refrigerant which is an HFC based refrigerant and with which it is more prone to corona discharge than with R.22, the apparatus including a first stop output device of compressor (23) to stop the operation of the compressor (1) if a pressure detected by the second pressure detector (13) has become less than or equal to a predetermined value that indicates that the compressor will perform vacuum operation. 3. A refrigerated apparatus as claimed in claim 1, including a temperature detector (24) in the compressor discharge tube (1), and an outlet device Compressor stop (26) to calculate a degree of superheating in the compressor discharge tube based on values detected by the first pressure detector (16), the temperature detector (24), and the detector device of cyclic refrigerant composition (15), and to stop the operation of the compressor (1) if a state in which the degree of superheat is less than or equal to a predetermined value has continued for a predetermined period of time. 4. A refrigerated apparatus as claimed in claim 1, including: a temperature detector (28) to detect a temperature of a refrigerant machine oil in the compressor (one); Y a compressor stop output device (29) to stop compressor operation (1) if a value detected by the temperature detector (28) it has become greater or equal than a default value, and if the state in which the value detected is greater than or equal to the default has continued for a predetermined period of time. 5. A refrigeration apparatus as claim in claim 1, including: a temperature detector (28) to detect a temperature of a refrigerant machine oil in the compressor (one); Y a compressor stop output device (30) to stop the operation of the compressor (1) if a difference between a temperature detected by the temperature detector (28) and a gas saturation temperature at a pressure detected by the second pressure detector (13) with a composition of the refrigerant detected by the composition detecting device cyclic (15) has become less than or equal to a value default, and if this status has continued for a period of default time